Means for clamping pipe sections

ABSTRACT

An internal clamping apparatus simultaneously engages the inner periphery of adjacent pipe ends in such a manner as to apply radially outward pressure thereto for reforming the ends into substantially identical circular configurations, regardless of any existing deformation in the pipe. The two reformed pipe ends are securely retained in an abutting position by the clamping means during an entire girth welding operation or the like at the pipe joint. Subsequent to the welding of the pipe joint, the internal clamping apparatus may be moved longitudinally along the pipe line to the position of the next pipe joint to be welded, and the entire operation may be repeated.

United States Patent Stanley Aug. 7, 1973 [54] MEANS FOR CLAMPING PIPE SECTIONS 3,330,02l 7/1967 .lacobsen 29/200 P 75 Inventor: Richard Carl Stanle T l a, Okl 1 u S a Prjmary ExaminerThomas H. Eager [73] Assignee: Midwestern Specialties, Ltd., Tulsa, AttorneyWilliam S. Dorman Okla.

[22] Filed: Aug. 2, 1971 ABSTRACT An internal clamping apparatus simultaneously en- [21] Appl' l68l87 gages the inner periphery of adjacent pipe ends in such Related U.S. Application Data a manner as to apply radially outward pressure thereto [62] Division 0fSer N 77 41 Nov, 25 19 p No, for reforming the ends into substantially identical cir- 3,681,560. cular configurations, regardless of any existing deformation in the pipe. The two reformed pipe ends are se- [52] U.S. Cl 29/200 B, 29/200 P, 228/44 curely retained in an abutting position by the clamping [51] Int. Cl. B23p 19/00 means during an entire girth welding operation or the [58] Field of Search 29/200 B, 200 P, like at the pipe joint. Subsequent to the welding of the 29/200 R, 203 P, 200 J; 228/44, 4 pipe joint, the internal clamping apparatus may be moved longitudinally along the pipe line to the position [56] References Cited of the next pipe joint to be welded, and the entire oper- UNITED STATES PATENTS anon y be l'epeated- 2,6l5,413 10/1952 Adams et al. 29/200 P X 7 Claims, 22 Drawing Figures PATENTEI] AUG 7 I975 sum 01 or 1 INVENTOR RICHARD c. STANLEY ATTORNEY PATENTEDAUG 1191:. 3,750,255

sum o2ur13 VENTOR. RICHA C. STANLEY AT TORNEY PATENIEB AUB H975 3,750,255

sum 03 nr 13 FIG. 3 INVENTOK RICHARD C. STANLEY ATTORNEY PATENIEU AUG 7 73 SHEET on my 13 Illllllll III-Ill I 1| IRE uh I l I l: I

MIL *m HIP m INVENTOR. RICHARD c. STANLEY MXM ATTORNEY PATENIEDAUE H915 3.750.255

I sum 05 [1F 13 IIIIFJ INVENT OR. RICHARD C. STANLEY ATTO R NEY PATENTED AUG 7 I975 sum as or 13 m m F INVENTOR. RICHARD C. STANLE ZQMM.

ATTOR NE Y PATENTEU 3.750255 SHEET 09UF13 FIG. l5

INVENTOR. RICHARD C. STANLEY ATTOR NEY I PAIENIEUMH. 71m

sum 10 or 13 ATTORNEY PATENTEW 3.750.255

sum 11UF 13 HIHIHIIIE IHIII l8 FIG I7 I66 '8 RICHARD C. STANLEY ATTORNEY INVENTOR.

PATENIEIJAUB 1 I975 SHEET 12 0F 13 I I I I 500 484 FIG. I8

FIG. I9

FIG.2O

ATTORNEY PATENTEDAUG 3,750,255

sum 13BF13 INVENTOR. RICHARD C. STANLEY ATTORNEY MEANS FOR CLAMPING PIPE SECTIONS This application is a division of my co-pending appication now US. Pat. No. 3,681,560, issued Aug. 1, 1972, Ser. No. 778,416, filed Nov. 25, I968, This invention relates to improvements in pipe welding method and means and more particularly, but not by way of limitation, to a novel method and means for internal clamping of adjacent pipe ends during external circumferential welding of the pipe joint.

Pipe lines normally extend throughout relatively long distances and across terrain which is often remote. In the usual construction of a pipe line, a plurality of pipe sections are initially disposed in tandem relation, and the adjacent ends of the pipe sections are placed in abuttment and welded together. Of course, it is important that the welded joints be of an extremely high quality to assure an efficient handling of the products transported thereby, and to increase the life of the pipe line while reducing maintainence thereof. The welding of the pipe joints in the field has long been a problem in the industry, and much time and expense has been involved in an effort to solve the problem.

The present invention contemplates a novel clamping means for an improved method and means for welding pipe joints in the field, and includes two complementary overall steps for providing the increased welding efficiently at each joint. The internal pipe clamping apparatus of the present invention has been particularly designed and constructed for simultaneously applying radially outward pressure on each of the abutting pipe ends for restoring a substantially true circular configuration for the pipe ends to be united or welded. The clamping apparatus forms the pipe ends into a substantially identical configuration and securely holds the ends so formed in an efficient abutting position during the welding operation. An external welding apparatus is then utilized for providing a circumferential welding operation around the joint determined by the abutting pipe ends. The welding apparatus is provided with a pair of carriages independently movable around the circumference of the pipe. Each carriage is provided with a plurality of aligned welding heads so mounted on the respective carriage whereby one of said heads applies an initial layer or welding material in the pipe joint, and the next succeeding welding head applies the next succeeding layer of welding material on the first applied layer, with the time interval between the two layers being at the optimum for assuring an efficient overall welding operation.

In addition, each of the carriages move separately about the circumference of the pipe for performing simultaneous welding operations at difierent positions in the pipe joint. One of the carriages initially is positioned at and moves around the circumference to a position of approximately 180 during the welding operation. Simultaneously, the second carriage is initially positioned at 270 and moves around the pipe to a position of 180 during the welding operation, then quickly moves to the 360 and again begins the welding operation while moving from 360 back to the initial 270 position. This results in a complete circumferential weld at the pipe joint, and efficiently percentage the welding apparatus at all times.

The unwelded pipe joint is usually in the form of a V- shaped circumferential groove between the abutting ends of the pipe sections and the welding operation fills the groove with welding material for uniting the pipe sections. Each of the welding heads may be independently oscillated during the welding operation for increasing the overall results of the apparatus and method. The welding head providing the first pass or application of welding material in the bottom of the groove is oscillated in a relatively slight movement whereas the next succeeding welding head is oscillated in a greater movement. Each welding head may be suitably adjusted whereby the oscillation thereof will be at the optimum in accordance with the particular welding requirements thereof. In addition, the plane of the weld groove may not be exactly perpendicular to the longitudinal axis of the pipe, or indeed, may deviate from any plane surface at all. In order to overcome this disadvantage, a guide wheel is provided which rolls along or rides in the groove and maintains the welding heads in alignment with the groove regardless of irregularities in the path of the groove. Subsequent to the completion of the welding at one pipe joint, the clamping apparatus and welding apparatus may be moved longitudinally through and along the pipe to the next pipe joint and the operation may be repeated.

The resulting welded joint accomplished through the method and means of the present invention have proven to be excellent. X-ray inspection has shown the welded joints are substantially free from holidays and sections cut through the material of the weld and adjacent material of the pipe sections have shown an excellent quality in the resulting weld. It is to be noted that the superior clamping method and means for reforming the adjacent pipe ends and aligning and clamping the pipe ends in abutting relationship prior to and during the welding operation are an important step in the overall results obtained in the final welding operation. Any misalignment of the abutted pipe ends or any nonconformity therebetween would decrease the end result of the welding operation. Thus, the novel and increased efficiency of results possible through practice of the present invention include the combined steps of performing the pipe ends into a substantially circular configuration by the internal clamping means, efficient aligning and clamping the abutting pipe ends prior to and during the welding operation, and performing the external welding operation by simultaneously and sequentially welding the joint in separate welding layers or operations while passing a plurality of welding heads circumferentially around the pipe joint. The novel pipe clamping means is simple and efficient in operation and economical and durable in construction.

It is an important object of this invention is to provide a novel method and means for facilitating welding pipe joints wherein the adjacent pipe ends to be welded are initially formed into substantially true mating circular configurations for improving the overall welding results.

Another object of this invention is to provide a novel method and means of welding a pipe joint wherein the abutting pipe ends are securely clamped and aligned prior to and during the welding operation.

Other and further objects and advantageous features of the present invention will hereinafter more fully appear in connection with a detailed descripton of the drawings in which:

FIG. 1 is a side elevational view of a pipe welding apparatus embodying the invention.

FIG. 2 is a front elevational view of a pipe welding apparatus embodying the invention with certan portions eliminated for purposes of illustration.

FIG. 3 is a rear elevational view of a pipe welding apparatus embodying the invention and disposed around a pipe section with the pipe being depicted in dotted lines.

FIG. 4 is a side elevational view of the track and saddle member ofa pipe welding apparatus embodying the invention.

FIG. 5 is a plan view of a portion of the support structure for the welding heads.

FIG. 6 is a side elevational view of a portion of the support structure shown in FIG. 5 and particularly indicates the adjustng mechanism for the welding apparatus.

FIG. 7 is a perspective view of a support base member utilized in the invention.

FIG. 8 is an enlarged elevational view particularly depicting the guide wheel means in association with a welding head.

FIG. 9 is an elevational view of the yieldable attaching means for the guide roller of the welding apparatus.

FIG. 10 is a sectional view taken on line 10-10 of FIG. 9 depicting the adjusting arrangement for the guide roller mechanism of the welding apparatus.

FIG. 11 is a bottom view of a support member of the welding apparatus.

FIG. 12 is a sectional view taken on line 12-12 of FIG. 11.

FIG. 13 is an enlarged sectional view taken on line 13-13 of FIG. 6.

FIG. 14 is a sectional elevational view of a pipe section having an internal clamping apparatus member the invention disposed therein.

FIG. 15 is a transverse sectional view of a pipe section having an internal clamping apparatus member the invention disposed therein.

FIG. 16 is composite transverse sectional view of a pipe section having the clamping mechanism disposed therein with the lower right hand portion of the figure depicting a clamp as modified for large diameter pipe sections.

FIG. 17 is a sectional view taken on line 17-17 of FIG. 16 and depicting the clamping portion of the clamping apparatus disposed at the joint with the upper half of the figure depicting the clamp in a clamping position and the lower half of the figure depicting the clamp in a relaxed position.

FIG. 18 is a side elevational view of a roller member of the clamping apparatus for propelling the clamping apparatus through the interior of the pipe.

FIG. 19 is a plan view of the roller depicted in FIG. 18.

FIG. 20 is a view taken on line 20-20 of FIG. 18.

FIG. 21 is a sectional view taken on line 21-21 of FIG. 14.

FIG. 22 is an elevational view of a pipe joint with a schematic depiction of an internal clamping apparatus, an external welding apparatus in association therewith embodying the invention.

Referring to the drawings in detail, and particularly FIGS. 1 through 13, an external pipe welding apparatus in generally indicated at 10 which comprises a plurality of welding heads 12 adjustably mounted on a carriage device 14 in a manner as will be hereinafter set forth. The carriage device 14 is movably secured or mounted on a circular or annular track 16 which encircles a pipe section 18, or other tubular member, or the like. The track 16 is carried by or secured to a saddle member 20 which straddles a portion of the outer periphery of the pipe 18 and secures the track 16 thereon in a manner precluding rotation of the track 16 with respect to the longitudinal axis of the pipe 18. The carriage 14 moves or is propelled around the track 16 during a pipe joint welding operation for moving the welding heads 12 around the pipe for providing a circumferential, in place, welding operation, as will be hereinafter set forth.

The pipe welding apparatus 10 as depicted herein preferably comprises three welding heads 12a, 12b, and 12c, as particularly shown in FIG. 2. However, it is to be noted substantially any desired number of welding heads may be used. By way of example, an efficient welding operation has been performed utilizing two welding heads following the same general procedure as will be hereinafter set forth. The welding heads 12a, 12b, and 12c may be of any suitable type and as shown herein are of the MIG (metallic inert gas) type.

The welding heads 12 are each independently mounted on a base member generally indicated at 22 whereby the position of each welding head 12 may be independently adjusted and each head 12 may be independently oscillated during the welding operation for a purpose and in a manner as will be hereinafter set forth. The base 22 is bolted or otherwise secured to a pair of shoulder blocks 24 and 26 which are suitably secured to the inner faces of a pair of spaced side plates 28 and 30 having a rear or back filler plate secured therebetween. The shoulder blocks 24 and 28 extend inwardly from the side plates 28 and 30 as particularly shown in FIG. 5 and the base 22 is provided with upstanding boss or flange portions 32 and 34 extending along the opposite edges thereof as viewed in FIG. 7 whereby bolts or the like 36 may be utilized for securing the base 22 to the shoulders 24 and 26 and between the side plates 28 and 30. In addition, a pair of spaced upwardly extending block members 38 and 40 are provided on the upper surface of the base member 22 as viewed in FIGS. 5 and 7 whereby bolts 42 or the like, may be utilized for facilitating securing of the base 22 to the shoulders 24 and 28. The shoulders 24 and 26 each support a suitable control motor 44 and 46 respectively and a third similar control motor 48 is interposed therebetween and supported on a plate 50 which is bolted or otherwise secured on the blocks 38 and 40, such as by the bolts 52. The motors 44, 46, and 48 may be of any suitable type and are preferably a Boehm control motor which is utilized for oscillating the welding heads 12 as will be hereinafter set forth.

The base 22 is provided with a plurality (preferably three) of recesses 54a, 54b, and 540 as particularly shown in FIG. 7 disposed in substantial alignment with the welding heads 12a, 12b, and 12c, respectively, the recesses 54a, 54b, and 540 being provided for slidably receiving the welding head support apparatus 56 of the respective welding head. Each support member 56 for the welding heads 12 is substantially identical and only one of the support structures 56 will be set forth in detail herein. whereby the welding heads 12 may be adjustably secured to the base 22 in any suitable manner, the securing device 56 depicted herein comprises a substantially tubular split nozzle clamp 58 adapted to be secured around the welding head or welding nozzle 12. A radially outwardly projected rod or arm member 62 is carried sliding the clamp 58 and extends from the clamp 58 into connection with a sliding block member 64. The slidng block member 64 is provided with a transversely extending recess 66 for receiving a complementary flange member 68 provided on a substantially L-shaped bracket member 70. The sliding block 64 may be positioned with respect to the flange 68 as desired for locating the lateral position of the respective welding head 12 with respect to the pipe 18 and the block 64 may then be securely locked in position by means of a cap screw 72 or the like which extends through the bracket 70 and into engagement with the block 64.

A rod member 74 is secured to the bracket 70 and is journalled within an oscillator clamping bracket 76. The bracket 76 is preferably of the split sleeve type and may be secured around the rod 74 by means of the screws 78 or the like. A plate member 80 is secured to the upper end or upper portion of the clamp 76 as viewed in FIG. 6 and is suitably disposed within longitudinally extending grooves or recesses (not shown) provided in downwardly extending blocks or hanger members 82 which are secured in the opposite longitudinal side walls of the respective recess 54. The blocks or hangers 82 are preferably constructed from Micarta and may be secured within the respective recess 54 in any suitable manner such as by bolting or the like and the plate 80 is longitudinally slidable with respect thereto. The rod 74 may be pivotally adjusted within the clamp member 76 to provide the desired angular position for the respective welding head 12 with respect to the pipe 18 and the rod 74 may then be securely clamped in the selected positionby the screw member 78 as is well known.

A rod 84 is carried by the plate 80 and extends downwardly therefrom as viewed in FIG. 6. A substantially spherical ball joint member 86 is journalled on the rod 84 and a nut 88 is threadedly secured to the outer extremity of the shank 84 for precluding accidental loss of the ball joint 86. A projection member 90 extends from the ball joint into engagement with the opposite end of the rod 74. An internally threaded sleeve 92 bears against the outer periphery of the ball joint 86 or is suitably connected thereto and extends in a direction away from the rod 84 which is opposite from the heads 12. A threaded insert member 94 extends into the sleeve 92 and is carried by a substantially spherical ball joint 96. The ball joint 96 is journalled on a crank pin member 98 which is carried by a crank arm follower 100 (FIG. 13) which in turn is carried by a crank shaft 102 which extends through an aperture 104 provided in the base member 22. The crank shaft 102 may be journalled within the aperture 104 in any suitable manner and is shown in FIG. 13. A pair of aligned bushing sleeves 106 and 108 are disposed around the outer periphery of the crank shaft 102 and provide an inner race for a pair of suitable spaced ball bearings 110 and 112 which are disposed within a flanged sleeve 114 secured within the aperture 104 by a lock washer 116.

A suitable sprocket 118 is keyed or otherwise secured to the upper end of the crank shaft 102 as viewed in the drawings for transmitting rotation to the crank shaft. Whereas the sprocket may be of any suitable type, it is preferable to provide a single structure sprocket complementary to a similar sprocket 120 secured to a rotatable drive shaft 122 which extends from a suitable gear boss 124 wherein the drive shaft 122 is coupled with the drive shaft (not shown) of the motor 44 whereby the drive shaft 122 will be driven or rotated by the motor 44. Rotation is transmitted from the sprocket to the sprocket 118 by a suitable chain, belt, or the like (not shown) as is well known. Upon actuation of the motor 44, rotation is transmitted from the sprocket 120 to the sprocket 118 for rotating the crank shaft 102 whereby the crank pin 98 is rotated in a cam action as is well known for transmitting oscillatory or reciprocal motion to the plate 88 through the connection members 94, 92, and 88. Of course, the

length of the stroke or oscillatory movement of the plate 80 may be adjusted by the threaded connection between the sleeve 92 and pin 94. This oscillatory motion is transmitted to the clamping member 58 and, of course, to the welding head 12 carried thereby. It will be apparent that the frequency and magnitude of the oscillation of each welding head 12 may be independently adjusted to provide the optimum welding operation in a sequential welding process as will be hereinafter set forth.

Referring now to FIGS. 1 and 2 a motor mounting bracket 126 is secured between the side plates 28 and 30 and is provided with a suitable wire guide connector bracket or block 128 for each welding head 12. The connector bracket 128 is preferably the well known or standard Airco connector block whereby the usual curved arcuate wire guide tubing 130 may be secured or connected between the welding head nozzles and the respective connector blocks. A connecting arm 132 is suitably secured to the bracket 126 in association with each connector block 128 and extends in opposite directions therefrom for rotatably supporting a wire spool assembly 134 whereby welding wire may be directed from the spool 134 through the connector blocks 128 and through the welding tube guide 130 to the welding nozzles as is well known. In addition, a suitable motor 136 is mounted on the mounting bracket 126 in association with each wire spool assembly 134 for driving or feeding the wire to the welding nozzles during a welding operation, as is well known. Of course, the motors 136 may be of any well known type, and as shown herein are preferably of the type known as a Boehm wire feed motor.

The base 22 is movably secured to the carriage de vice 14 whereby the base 22 and elements carried thereby may be adjusted to substantially any desired spacing from the carriage 14. An arm member 138 is provided on the carriage device 14 and extends outwardly therefrom in a direction toward the base 22, as particularly shown in FIG. 1. The arm 138 is provided with an elongated cam recess 140 for receiving a roller member 142 therein, said roller 142 being journalled in a downwardly extending flange 144 provided on the lower surface of the base 22 as viewed in FIGS. 2 and 5. The roller member 142 normally rides freely within the recess 140 and may be securely locked in substantially any desired position therein by any suitable locking means, such as by the locking means generally indicated at 146 in FIG. 1 for locking the assembly 10 during shipping or transporting of the device between joints to be welded.

A downwardly extending boss 148 is provided on the lower surface of the base 22 as viewed in the drawings, and extends along the side edge thereof oppositely disposed from the arm 138. The boss 148 is provided with a centrally disposed bore 150 extending longitudinally therethrough as particularly shown in FIGS. 11 and 12. A plurality of spaced bushing or bearing sleeves 152 and 154 are disposed within the bore 150 and are preferably spaced apart by a spacer sleeve 156, and retained within the bore 150 by suitable lock washers 158, or the like, as is well known. A plurality of balls 158 are disposed within each sleeve 152 and 154 and are interposed between the sleeves 152 and 154 and a slidable shaft 160 extending longitudinally through the sleeves. The halls 158 are retained in position in any well known manner, such as by the retainer rings 162. An enlarged head member 164 is secured to the outer end of the shaft 160 and is bolted, or otherwise secured to the carriage device 14, and remains immovable with respect thereto. It will be apparent that the boss 148 is freely slidable along the shaft 160, thus facilitating moving of the base 22 in directions toward or away from the carriage device 14.

A pipe joint to be welded, such as shown at 166 in FIGS. 1 and 22, is formed between the abutting ends of adjacent pipe sections 18 disposed in substantial longitudinal alignment. The ends of the pipe sections 18 are normally bevelled, as is well known, and the cross sectional configuration of the pipe joint 166 is usually substantially V-shaped, as depicted herein. Referring now to FIGS. 1, 2, 8, 9, and 10, a guide roller assembly generally indicated at 168 is carried by the base member 22 and comprises a guide roller or wheel member 170 having an outer periphery of a configuration generally complementary to the cross-sectional configuration of the pipe joint 166. The guide roller or wheel 170 is provided for riding in the pipe joint 116 during a pipe welding operation for automatically retaining the welding heads 12 in alignment with the pipe joint for assuring an efficient welding operation in a manner as will be hereinafter set forth. The roller 170 is journalled on a shaft or pin 172 in any suitable manner, such as by a roller bearing 174, and is retained on the shaft 172 by a lock nut 176, or the like. The pin 172 is suitably secured to a guide arm 178 which is preferably of an angular configuration as particularly shown in FIGS. 2 and 9 to provide a substantially bell crank action for the support of the roller 170.

The guide arm 178 is pivotally secured at 180 to an arm retainer plate 182, with the pivot point 180 providing a fulcrum for the arm 178. The retainer plate 182 is carried by a sleeve or tubular member 184, and is rigidly secured thereto in any well known manner. Upon assembly of the guide roller mechanism 168, the retainer plate 182 is preferably disposed at an angle of approximately 30 with respect to the center line of the pipe as indicated at A in FIG. 9. A pin 184 is secured to the exposed surface of the retainer arm 182 and extends substantially perpendicularly outward therefrom for receiving one end of a suitable compression spring 186. The opposite end of the spring 186 is anchored at a second pin 188 provided on the exposed face of the arm 178. The spring 186 constantly urges the arm 178 in a counterclockwise direction about the fulcrum 180, as viewed in FIG. 9, and thus constantly urges the wheel 170 in a direction toward the pipe joint 166 in which it is exposed.

A locking pin 190 is slidably disposed within the central bore 192 of a pin housing 194 which is threadedly secured to the arm 178 as shown in FIG. 10. The bore 192 is enlarged at 195 to provide a shoulder 196 whereby a helical spring 198 is disposed around the pin 190 is contained between the shoulder 196 and an annular shoulder 200 on the pin 190 and thus constantly urges the pin 190 in a right hand direction as viewed in FIG. 10. A head member 202 is secured to the left hand end of the pin 190 as shown in FIG. 10 for limiting the right hand movement of the pin 190. In addition, the head 202 may be manually grasped for moving the pin 190 in a left hand direction against the action of the spring 195. When it is desired to release the engagement of the guide wheel with the pin joint 166, the pin may be retracted within the bore 192 and the arm 178 may be pivoted in a clockwise direction as viewed in FIG. 9 whereby the pin 190 will be moved into alignment with a bore or recess (not shown) provided in the retainer 182. The pin 190 may be disposed within the recess for locking the wheel 170 in a position out-of-engagement with the pipe joint. This is particularly advantageous when the pipe welding apparatus 10 is to be moved from the site of one pipe joint 166 to the site of another pipe joint 166, as will be hereinafter set forth.

The sleeve or tube member 184 is slidably disposed on a tube 204 in a manner as will be hereinafter set forth. The tube 204 is provided with an outwardly extending circumferential flange member 206 on the outer end thereof. The flange 206 is secured in any well known manner, such as the bolts 210, to a substantially circular flange member 208 provided integral with or rigidly secured to the base 22. The sleeve 184 is provided with at least one longitudinally extending in the side wall thereof having one end open for receiving a guide pin 214 therein. The pin 214 is carried by the inner sleeve 204 and cooperates with the slot 212 for facilitating reciprocal movement of the outer sleeve 182 with respect to the inner sleeve 204.

A web member 216 is rigidly secured within the inner sleeve 204 and is provided with a central threaded bore 218 for receiving a threaded stud member 220 therethrough. The stud member 200 extends outwardly through an aperture 222 provided in the retainer arm 182 and is rigidly connected with a suitable knob member 224 by a set screw 226, or the like. An outwardly extending circumferential flange 228 is provided on the stud member 220 and is interposed between the knob member 224 and the threaded end portion for engaging an annular shoulder 230 provided conterminous with the bore 222 whereby the stud member 220 may be rotated upon manual rotation of the knob 224, but is retained against longitudinal movement with respect to the outer sleeve 184 by the engagement of the shoulder 22 and flange 228, and further by the engagement of the knob 224 with the outer face of the retainer arm 182. Thus, rotation of the stud 220 in one direction will cause the stud 220 and outer sleeve 184 to move in a right hand direction with respect to the inner sleeve 204 as viewed in FIG. 10, and rotation of the stud 220 in an opposite direction will cause the sleeve 184 to move in a left hand direction with respect thereto. It will be apparent that manual rotation of the knob 224 permits an adjustment of the position of the guide wheel 170 for assuring an alignment of the wheel 170 and the pipe joining 166 during the installation of the pipe welding apparatus 10 at the pipe joint for beginning a welding operation.

Referring now to FIGS. 1, 3, and 4, the carriage device 14 comprises a suitable support plate 240 having a pair of spaced outwardly extending support arms 242 and 244 adapted to span a portion of the track 16 as will be hereinafter set forth in detail. A plurality of bracket members 146 are bolted or otherwise secured to the plate 240 in the proximity of spaced elongated apertures 248 provided in the plate 240 as particularly shown in FIG. 3. Each bracket 246 is provided with an arm member 250 (FIG. 1) which extends through the respective aperture 248. A first roller member 252 is suitably journalled on each bracket 246 and extends through the respective slot 248 for engaging a first cylindrical portion of the track 16. The roller 252 is adjustably secured to the bracket 246 for a purpose as will be hereinafter set forth. A second roller member 254 is suitably journalled on the arm 250 of each bracket 246, with the second roller 254 being disposed in a plane substantially perpendicular with respect to the plane of the first roller 252 whereby the second roller engages an annuar portion of the first roller whereby the second roller engages an annular portion of the track 16 as will be hereinafter set forth.

A plurality of similar bracket members 256 are bolted or otherwise secured to the plate 240 and spaced from the first brackets 246 as particularly shown in FIG. 3. Each of the brackets 256 is secured in the proximity of spaced apertures 258 provided in the plate 240. Each bracket 256 is provided with an arm member 260 (FIG. 3) which extend through the respective slot 258. A first roller member 262 is journalled on each of the brackets 256 and extends through the respective slot 258 for engagement with a second cylindrical portion of the track 16. The roller 262 is adjustably secured to the bracket 256 for a purpose as will be hereinafter set forth. A second roller 263 is suitably journalled on the arm 260 of each bracket 256, with the plane of the second roller 263 being disposed substantially perpendicular with respect to the plane of the first roller 262 whereby the second roller 263 engages an annular portion of the track 16, as will be hereinafter set forth in detail.

The entire carriage 14 moves circumferentially around the track 16, and as shown herein, a motor 264 is carried by the carriage 14 for providing the power or means for moving the carriage 14 with respect to the track 16. The motor 264 may be of any suitable type, and as shown herein is preferably the Boehm gear motor type. The motor 264 is suitably mounted on a support bracket 266 which in turn is mounted on or secured to the arm 244 of the support bracket plate 240. The output or drive shaft 268 of the motor 264 drives a sprocket member 270 which is connected with a pair of spaced sprockets 272 and 274 by a suitable chain 276, or the like, (FIG. 3) which extends around the outer periphery of the sprocket 270 and the sprockets 272 and 274, and over an adjustable idler sprocket drive gear member 278. The position of the idler sprocket 278 may be adjusted as required for maintaining the proper tension in 276 for efficiently driving or rotating the sprockets 272 and 274.

Each sprocket 272 and 274 is secured to or connected with similar drive gears 280 and 282 through a drive shaft 284 and 286, respectively, whereby rotation of the sprockets 2'72 and 274 is transmitted to the gears 280 and 282. The gears 280 and 282 are disposed in meshing engagement with a ring gear 288 which extends around the outer periphery of the track 16. Thus, upon rotation of the sprocket 270 by the actuation of the motor 264, the sprockets 272 and 274 .will be rotated by the drive chain 276, and rotation will be simultaneously transmitted to the drive gears 280 and 282. The ring gear 288 is integral with or rigidly secured to the stationary track 16, and cannot rotate with respect thereto. Thus, the rotation of the drive gears 280 and 282 which mesh with the ring gear 288 causes the entire carriage device 14 to move circumferentially around the track 16. Of course, the welding heads 12 are thus moved circumferentially around the track 16 and simultaneously moved circumferentially around the pipe 18 for performing a circumferential pipe joint welding operation, as will be more fully set forth in detail hereinafter.

The track 16 is of a generally annular configuration having an inner periphery of a diameter greater than the diameter of the outer periphery of the pipe 18. The track 16 is preferably severed at three spaced locations, as indicated by the lines 290, 292, and 294 in FIG. 3, thus providing three arcuate sections A, B, and C for the track 16. The section A as shown in FIG. 3 is substantially greater in circumferential length than the combined circumferential lengths of the sections B and C, but is not limited thereto. The sections B and C are secured to the opposite ends of the section A by suitable hinge members 296 and 298 whereby the sections B and C may each be pivoted in the direction indicated by the arrows 300 and 302, respectively, for opening of the track 16 to facilitate installation of the device 10 around the pipe section 18. The free ends of the sections B and C meet at the line 294 in the closed position of the track 16, as shown in FIG. 3, and any suitable locking or latching device (not shown) may be bolted across the abutting ends of the sections B and C, or otherwise span the ends of the sections for securely locking the track 16 in position around the pipe 18.

The track 16 may be of any suitable construction, and as shown herein is provided with an enlarged circumferential portion 304 having the ring gear 288 integral therewith or otherwise rigidly secured around the outer periphery therof. A pair of concentrically arranged inner and outer circular or cylindrical rail members 306 and 308 are provided in the annular member 304 and are open in a direction toward the carriage device 14 for receiving the rollers 252 and 262 therebetween. The rollers 252 bear against the outer periphery of the inner rail 308 and the roller members 262 bear against the inner periphery of the outer rail 306 as the carriage device 14 moves circumferentially around the track 16. Of course, the pressure of the rollers 252 and 262 against the rails 308 and 306, respectively, may be adjusted by adjusting the position of the rollers extending through the respective slots 248 and 258. In addition, an annular wall member 310 extends between the spaced rails 306 and 308, and the rollers 254 and 262 bear against or ride along the right hand surface of the wall 310 as viewed in FIG. 4 as the carriage device 14 moves circumferentially around the track 16. It will be apparent that the rollers 252 and 262 facilitate the circumferential movement of the carriage device 14 around the track 16 and maintain the carriage device 14 in the proper concentric relation in its movement around the track 16. In addition, the rollers 254 and 263 maintain the carriage device 14 against longitudinal or axial movement with respect to the track 16 in one direction and facilitates retaining of the carriage device 14 in position on the track 16.

As particularly shown in FIGS. 3 and 4, the saddle 20 is secured to the track 16 and extends longitudinally outward therefrom in a direction away from the carriage device 14 and welding heads 12. The addle 20 may be of substantially any suitable well known construction, and as shown herein comprises a plurality of longitudinally extending circumferentially spaced support posts 312 each having one end rigidly secured to the track 16 oppositely disposed from the annular member 304. A plurality of pipe straddling angular strap members 314 are secured between the posts 312 in any well known manner. In addition, a plurality of oppositely disposed downwardly extending side arm supports 316 are secured to the posts 312 and are longitudinally spaced therealong as shown in FIG. 4. A longitudinally extending connecting strap 318 is suitably secured between the outer ends of each adjacent pair of arms 316, and a roller support bracket 320 is secured to the opposed ends of each of the straps 318. A roller member 322 is journalled in each of the brackets 320 and are so arranged as to roll along the outer periphery of the pipe section 18 in a longitudinal direction. A belt or adjustable strap member (not shown) is normally secured between the strap member 318 and around the outer periphery of the pipe 18 extending below and between the straps 318 for securely clamping and retaining the saddle member 20 in position around the pipe 18, as is well known.

It is preferable to provide at least one roller 324 journalled in a bracket 326 which is suitably secured to the track 16, with the roller 324 being so arranged as to ride longitudinally along the outer periphery of the pipe section 18. It is further preferable to provide at least one similar roller (not shown) suitably secured to the outer edge of the straddle strap 314 and arranged for disposition against the outer periphery of the pipe in a manner similar to the roller 324. These rollers are transport rollers and cooperate with the rollers 322 for facilitating moving of the entire device longitudinally along the outer periphery of the pipe 18 for a purpose and in a manner as will be hereinafter set forth.

WELDING APPARATUS OPERATION When it is desired to weld a pair of adjacent pipe sections 18 in end to end relation, such as at a pipe joint 166, the welding apparatus 10 is disposed on one of the pipe sections 18 in the proximity of the pipe joint to be welded, with the welding heads 12 disposed in substantial alignment with the pipe joint. In order to install the apparatus 10 around the outer periphery of the pipe section 18, it is preferable to open the track 16 by pivoting the track sections B and C in the directions indicated by the arrows 300 and 302 whereby the track may be disposed around the pipe in a transverse direction. The rollers 322 and 325 of the saddle portion rest on the outer periphery of the pipe 18 and support the apparatus 10 from the pipe section in such a manner that the track 16 is substantially concentrically disposed with respect to the pipe section. The track sections B and C may then be pivoted in a reverse direction for closing thereof around the pipe 18, and shown in FIG. 3, and may be latched or securely locked in the closed position.

The carriage device 14 may be secured to the track 16 either prior to or subsequent to securing of the track and saddle around the pipe section, and the position of the rollers 252 and 262 with respect to the rails 308 and 306, respectively, may then be adjusted to assure an efficient contact therebetween. It is preferably to provide two of the carriage devices 14 and associated welding heads 12 on the track 16 with one of the carriages 14 being disposed as shown in FIG. 3, which will be hereinafter referred to as a 0 position, and with the other carriage disposed at substantially 270 position (clockwise) with respect thereto.

The angular disposition of the welding heads 12 of each carriage device 14 with respect to the pipe 18 may be adjusted as desired through the pivotal connection of the rod 74 (FIG. 6). Of course, the radial position of the heads 12 with respect to the pipe 18 may be adjusted in the usual manner, with the clamping member 58 being utilized for securely retaining the heads 12 in the desired position.

The guide wheel is disposed within the pipe joint 166 as shown in FIG. 1, and the positioningof the guide wheel 170 in the pipe joint automatically aligns the heads 12 with the pipe joint due to the connection between the guide wheel and the welding heads as hereinbefore set forth. Of course, the guide wheel 170 rides in the groove or pipe joint as the apparatus 10 revolves around the pipe 18, regardless of any deviation or irregularities of the plane of the pipe joint by virtue of the sliding connection of the base 22 with the carriage device 14. Thus, the welding heads 12 are maintained in substantial alignment with the pipe joint 166 as the apparatus 10 moves circumferentially around the pipe.

Each carriage 14 is propelled around the track 16 by actuation of the respective motor 264. Rotation of the drive shafts 268 of the motors 264 rotates the drive gears 280 and 282 for moving the gears 278 around the ring gear 288, thus moving the carriages 14 around the track 16. Of course, the speed of movement of the carriages 14 may be regulated by the speed of the motor 268, the ratio between the sprockets 270 and 272, and the ratio between the gears 280 and 282 and the ring gear 288, as is well known. The drive gears 280 and 282 are circumferentially spaced in such a manner that no drive connection or drive engagement is lost between that portion of the ring gear 288 in the vicinity of the severed portion or joints 290 and 292, thus assuring an efficient and even movement of the apparatus 10 around the pipe 18.

As hereinbefore set forth, one of the carriages 14 is disposed at the 0 position on the track 16, and the other of said carriages 14 is disposed on the track 16 at 270 in a clockwise direction with respect to the first carriage 14. The welding heads 12 of each carriage 14 perform substantially simultaneous and sequential welding operations at the joint 166, as will be hereinafter set forth in detail, as the carriages 14 move circumferentially around the pipe 18. At the initiation of the welding operation, the first carriage 14 is moved in a clockwise direction from the original 0 position through an arc of substantially 180', thus welding substantially one half the circumference of the joint 166. Simultaneously, the second carriage 14 is moved in a counterclockwise direction from the original 270 position through an arc of substantially 90 thus welding approximately one fourth the circumference of the joint 166. The operation of the welding heads 12 of the second carriage 14 is then interrupted momentarily or for a relatively short time period, and the second carriage is very rapidly moved in a reverse or clockwise direction through an arc of approximately 180 and to 

1. An internal clamping apparatus for abutting cylindrical members disposed in tandem relation and comprising housing means, wheel means journalled on the housing means for moving the apparatus longitudinally within the cylindrical member, propelling means operably connected with the wheel means for driving thereof, alternately expandable and retractable clamping means, said clamping means having a substantially cylindrical outer periphery in the expanded position thereof, double acting piston means carried by the housing means and operably connected with the clamping means, pressure means operably connected with said piston means for actuation of the piston means in one direction for expanding the clamping means into simultaneous pressure engagement with the inner periphery of the adjacent ends of the abutting cylindrical members for reforming of any distortion of the said ends and in a second direction for contracting the clamping means out of engagement with the inner periphery of the cylindrical members.
 2. An internal clamping apparatus as set forth in claim 1 wherein the clamping means and double acting piston means comprise first reciprocal piston means, second piston means concentrically arranged with respect to the first piston means, a plurality of radially reciprocal clamping members circumferentially disposed around one of said piston means, toggle means operably connecting each clamping element with the first and second piston means, said first and second piston means being operable in simultaneous but opposite directions to one position for actuation of the toggle means for moving the clamping elements radially outward and to a second position for actuation of the toggle means for moving the clamping elements radially inward.
 3. An internal clamping apparatus as set forth in claim 2 wherein the toggle means comprises a first hub member rigidly secured to one of said piston means for reciprocation simultaneously therewith, first link toggle means connected between the first hub and each clamping element, second hub means rigidly secured with said second piston means for reciprocation simultaneously therewith, second link toggle means connected between the second hub and each clamping element, said link toggle members operable upon said simultaneous but opposite reciprocation of said first and second piston means for moving the clamping elements alternately radially inward and outward.
 4. An internal clamping apparatus for abutting cylindrical members disposed in tandem relation and comprising housing means, wheel means journalled on the housing means for moving the apparatus longitudinally within the cylindrical member, propelling means operably connected with the wheel means for driving thereof, alternately expandable and retractable clamping means, said clamping means having a substantially cylindrical outer periphery in the expanded position thereof, double acting piston means carried by the housing means and operably connected with the clamping means, pressure means operably connected with said piston means for actuation of the piston means in one direction for expanding the clamping means into simultaneous pressure engagement with the inner periphery of the adjacent ends of the abutting cylindrical members for reforming any distortion of the said ends and in a second direction for contracting the clampinG means out f engagement with the inner periphery of the cylindrical members, each of said clamping elements comprising a substantially T-shaped clamping member, the cross member portion of the Tee being disposed outwardly and cooperating with the cross member portion of the remaining clamping members to provide said substantially cylindrical outer periphery for the clamping means, and each of said cross members being of a width sufficient for spanning the joint between the said adjacent ends of the abutting cylindrical members for simultaneous engagement with the inner periphery of each adjacent end and reforming thereof into complementary cylindrical configurations.
 5. An internal clamping apparatus for cylindrical members comprising housing means, alternately expandable and retractable clamping means, said clamping means having a substantially cylindrical outer periphery in the expanded position thereof, double acting piston means carried by the housing means and operably connected with the clamping means, pressure means operably connected with said piston means for actuation of the piston means in one direction for expanding the clamping means to provide a substantially continuous circular engagement with the inner periphery of the cylindrical member and into pressure engagement therewith for reforming any distortion of the cylindrical member and in a second direction for contracting the clamping means out of engagement with the inner periphery of the cylindrical member.
 6. An internal clamping apparatus as set forth in claim 5 wherein the clamping means and double acting piston means comprise first reciprocal piston means, second piston means concentrically arranged with respect to the first piston means, a plurality of radially reciprocal clamping members circumferentially disposed around one of said piston means, toggle means operably connecting each clamping element with the first and second piston means, said first and second piston means being operable in simultaneous but opposite directions to one position for actuation of the toggle means for moving the clamping elements radially outward and to a second position for actuation of the toggle means for moving the clamping elements radially inward.
 7. An internal clamping apparatus as set forth in claim 6 wherein the clamping elements each comprise a substantially T-shaped clamping member, the cross member portion of the Tee being disposed outwardly and cooperating with the cross member portion of the remaining clamping members to provide said substantially cylindrical outer periphery for the clamping means. 